JP4973066B2 - Compressor and operating method of compressor - Google Patents

Description

  The present invention relates to a compressor and a method for operating the compressor, and more particularly to a compressor in which a suction throttle valve is provided in the middle of a suction passage communicating with a suction chamber and a method for operating the compressor.

Conventionally, as a compressor, for example, a refrigerant compressor disclosed in Patent Document 1 is known.
In this type of compressor, before sending the refrigerant gas at the discharge pressure from the compressor to the external refrigerant circuit, the mist-like lubricating oil contained in the refrigerant gas is separated, and the separated lubricating oil is retained in the oil storage chamber and stored. A configuration is adopted in which the lubricating oil is supplied to the crank chamber.

In this compressor, the lubricating oil is always supplied from the oil storage chamber to the crank chamber during all operations from the maximum capacity operation at which the discharge capacity is maximum to the minimum capacity operation at which the discharge capacity is minimum.
For this reason, according to this technique, the lubricating oil can be supplied to the sliding portion of the compressor even in the operation under the high speed and low load condition in which the circulation flow rate of the refrigerant gas is reduced.

Further, in order to always supply the lubricating oil to the sliding portion, it is conceivable to supply the separated lubricating oil to the crank chamber via the suction chamber.
JP 10-311277 A

However, the compressor disclosed in Patent Document 1 has a problem that the lubricating oil is always supplied to the crank chamber even during the minimum capacity operation of the compressor.
When the lubricating oil is excessively stored in the crank chamber, frictional heat is generated by stirring when the rotating element in the compressor such as a swash plate stirs the lubricating oil at a high speed.

  Friction heat due to agitation leads to an increase in the temperature of the compressor, and the high temperature of the compressor may reduce the durability of various sealing members formed of, for example, a sliding portion in the compressor or a rubber material or a resin material. There is.

Furthermore, in the compressor after being stopped, the amount of lubricating oil stored in the oil storage chamber is small.
When the compressor is started from this state, all of the lubricating oil in the oil storage chamber is lost to the crank chamber or the suction chamber, which may cause a so-called gas path phenomenon in which the refrigerant gas at the discharge pressure returns to the crank chamber or the suction chamber. .

The present invention has been made in view of the above problems, and an object of the present invention is to appropriately supply the lubricating oil from the oil storage chamber according to the operating state of the compressor by utilizing the opening and closing of the suction throttle valve. The present invention provides a compressor that can be controlled and a method for operating the compressor.
The

To achieve the above object, according to the present invention, a housing is provided with a suction chamber into which a refrigerant gas is sucked through a suction port connected to an external refrigerant circuit, and the refrigerant gas is discharged by being connected to the external refrigerant circuit. a discharge chamber, a compressor and a lubricant storage chamber for storing the separated lubricating oil from the refrigerant gas in the discharge pressure discharged from the discharge chamber, the compressor further the suction chamber and the suction port a suction passage communicating, and suction throttle valve for adjusting an opening degree of the suction passage based on a differential pressure acting on the valve body, through the lubricating oil of the oil storage chamber upstream of the suction throttle valve in the suction passage characterized in that it includes a lubricating oil passage.

In the present invention, when the compressor is operated, the lubricating oil in the oil storage chamber is introduced to the upstream side of the suction throttle valve in the suction passage through the lubricant passage, but when the suction passage is blocked by the closing of the suction throttle valve, The supply of the refrigerant gas to the suction chamber through the suction passage is shut off, and the lubricating oil supplied to the suction passage through the lubricating oil passage is stored in the suction passage upstream of the suction throttle valve.
For this reason, even if the compressor is stopped, the separated lubricating oil can be prevented from being supplied to the crank chamber via the suction chamber, and is not excessively stored in the crank chamber.

In the above compressor, the lubricating oil passage may include an on-off valve that controls a flow rate of the lubricating oil in the lubricating oil passage.
Conventionally, in order to prevent a gas path, it has been necessary to reduce the diameter of the lubricating oil passage so that the lubricating oil does not return too much. Had to put a filter on.
In the present invention, since the flow rate of the lubricating oil can be controlled and throttled by the on-off valve, it is not necessary to reduce the diameter of the lubricating oil passage, and there is almost no possibility of foreign matter clogging, so that the number of filters required in the past is reduced. Can do.

Further, in the above compressor, the on-off valve may be a reed valve that opens and closes the lubricating oil passage according to a pressure difference between a pressure in the oil storage chamber and a pressure upstream of the suction throttle valve in the suction passage. .
In this case, the reed valve as the on / off valve is opened / closed according to the pressure difference between the pressure in the oil storage chamber and the pressure upstream of the suction throttle valve in the suction passage .
Even when the valve installation space is restricted, a simple structure is required for the on-off valve that opens and closes according to the pressure difference.

Further, in the above compressor, the lubricating oil passage has a first valve hole and a second valve hole that are opened and closed by the on-off valve, and the on-off valve in a closed state with respect to the first valve hole is The flow rate of the lubricating oil passing through the first valve hole is suppressed, and the on-off valve that is in a maximum open state with respect to the first valve hole closes the second valve hole and passes through the second valve hole. The flow rate may be suppressed.
In this case, the on-off valve that is closed with respect to the first valve hole suppresses the flow rate of the lubricating oil that passes through the first valve hole.
In addition, since the open / close valve in the maximum valve open state with respect to the first valve hole closes the second valve hole, the flow rate of the lubricating oil passing through the second valve hole is suppressed.
When the on-off valve opens at a position near the middle between the valve-closed state and the valve-opened state with respect to the first valve hole, the flow rate of the lubricating oil passing through the lubricating oil passage is maximized.
Therefore, the flow rate of the lubricating oil passing through the lubricating oil passage can be suppressed and the gas path can be prevented in a state where the lubricating oil separating ability is extremely low when the compressor is operated at the minimum capacity or when the operation is stopped.
Furthermore, although the refrigerant flow rate is low and the lubricating oil separation capacity is low, such as during high-load low-speed operation of the compressor, the discharge pressure becomes high due to the high load, and the pressure in the oil storage chamber and the upstream suction passage Even when the pressure difference from the pressure is large and the flow rate of the lubricating oil through the lubricating oil passage is large, the on-off valve can close the second valve hole to suppress the flow rate of the lubricating oil, and the gas path Can be prevented.

Further, in the above compressor, a gasket, a valve forming body that forms a suction valve or a discharge valve, and a valve plate are interposed between a housing member having a suction chamber and the cylinder block, and the first valve hole is It may be formed in the gasket, the second valve hole is formed in the valve plate, the reed valve is formed in the valve forming body, and a maximum opening degree may be defined by the valve plate.
In this case, the first valve hole is provided in the gasket, the second valve hole is provided in the valve plate, and the reed valve for opening and closing the first valve hole and the second valve hole is provided in the valve forming body. There is no need to add new parts to provide a valve.

Further, the present invention provides a housing, a suction chamber into which refrigerant gas is sucked through a suction port connected to an external refrigerant circuit, a discharge chamber connected to the external refrigerant circuit and from which refrigerant gas is discharged, An operation method of a compressor having an oil storage chamber for storing lubricating oil separated from a refrigerant gas having a discharge pressure discharged from a discharge chamber, wherein the suction port and the suction are based on a differential pressure acting on a valve body A suction throttle valve provided in a suction passage communicating with the chamber is opened and closed, the separated lubricating oil is passed to the upstream side of the suction throttle valve in the suction passage, and the lubricating oil is opened by opening the suction throttle valve. The suction throttle valve is supplied to the suction chamber, and the supply of the lubricating oil to the suction chamber is suppressed by closing the suction throttle valve.

In this case, when the suction throttle valve opens the suction passage, the lubricating oil in the oil storage chamber is introduced into the suction chamber through the lubricant passage, the suction passage, and the suction throttle valve.
On the other hand, when the suction throttle valve closes the suction passage, the lubricating oil guided to the upstream side of the suction throttle valve through the lubricating oil passage is stored on the upstream side of the suction throttle valve.
For this reason, when the suction throttle valve closes the suction passage, the separated lubricating oil is not supplied to the suction chamber or the crank chamber.

According to the present invention, by utilizing the opening and closing of the suction throttle valve, a method of operating a compressor and the compressor can be appropriately controlled according to the supply of lubricating oil from the oil reservoir to the operating state of the compressor Can be provided.

(First embodiment)
Hereinafter, a compressor according to a first embodiment will be described with reference to FIGS.
FIG. 1 is a longitudinal sectional view showing the structure of a clutchless variable displacement compressor according to the first embodiment, and FIG. 2 is a longitudinal section showing the main part of the variable displacement compressor according to the embodiment of the present invention. Surface.
FIG. 3 is a longitudinal sectional view of the main part showing the operation of the suction throttle valve and the flow of lubricating oil when the capacity control valve is closed, and FIG. 4 is the operation and lubrication of the suction throttle valve when the capacity control valve is opened. It is a longitudinal cross-sectional view of the principal part which shows the flow of oil.
For convenience of explanation, the left side of the compressor in FIG.

As shown in FIG. 1, a front housing 12 is joined to one front end of the cylinder block 11, and a rear housing 13 is joined to the other rear end.
A space defined by the cylinder block 11 and the front housing 12 constitutes a crank chamber 14.

A rotating shaft 15 penetrating the crank chamber 14 is rotatably supported by the cylinder block 11 and the front housing 12.
The front end of the rotating shaft 15 protrudes to the outside of the front housing 12 as a protruding end, and this protruding end receives a rotational force transmitted from a driving source (not shown) such as an engine or a motor of the vehicle (not shown). Z)).
In this embodiment, a configuration in which engine power is always transmitted to the rotating shaft 15 is adopted, and the compressor is a clutchless type.
A rotating shaft 15 in the crank chamber 14 is provided with a swash plate 17 to which the rotating support 16 is fixed and engaged with the rotating support 16.

The swash plate 17 has a rotary shaft 15 passing through a through hole 18 formed at the center of the swash plate 17, and a guide pin 19 formed to protrude from the swash plate 17 is formed on the rotary support 16. The guide hole 20 is slidably fitted.
The swash plate 17 rotates integrally with the rotary shaft 15 based on the relationship of the insertion of the guide pins 19 into the guide holes 20.
The swash plate 17 is supported by the rotary shaft 15 so as to be able to slide in addition to being slidable in the axial direction of the rotary shaft 15 by sliding of the guide pins 19 with respect to the guide holes 20.
A thrust bearing 21 is provided on the front inner wall of the front housing 12, and the rotary support 16 is slidable with respect to the front housing 12 via the thrust bearing 21.

A plurality of cylinder bores 22 formed around the rotation shaft 15 are arranged in the cylinder block 11, and pistons 23 are slidably accommodated in the individual cylinder bores 22.
The front end of each piston 23 is engaged with the outer periphery of the swash plate 17 via a shoe 24, and when the swash plate 17 rotates together with the rotary shaft 15, each piston 23 moves in the axial direction in the cylinder bore 22 via the shoe 24. Move back and forth.

Further, a flange member 34 is joined to the upper outer periphery of the cylinder block 11, and an oil storage chamber 35 in which lubricating oil is stored is formed by the flange member 34 and the cylinder block 11.
The oil storage chamber 35 stores the lubricating oil from which the mist-like lubricating oil contained in the refrigerant gas at the discharge pressure is separated by an oil separator (not shown).
The oil separator is installed in a refrigerant gas passage (not shown) connecting between a discharge chamber 27 and an external refrigerant circuit (not shown) described below.
The oil storage chamber 35 is disposed above a suction throttle valve 40 described later.

A suction chamber 26 is formed in the center of the rear housing 13 so as to face the valve forming mechanism 25, and a discharge chamber 27 is formed on the outer peripheral side of the suction chamber 26 so as to surround the suction chamber 26.
As shown in FIGS. 1 and 2, a partition wall 13 a formed in the rear housing 13 separates the chambers 26 and 27.
In the cylinder block 11 and the rear housing 13, a communication path 28 that connects the crank chamber 14 and the discharge chamber 27 is formed.
A displacement control valve 29 composed of an electromagnetic valve is disposed in the communication path 28.
The cylinder block 11 is formed with an extraction passage 30 that always communicates the crank chamber 14 and the suction chamber 26.

A suction port 31 exposed to the outside is formed in the rear housing 13, and the suction port 31 and the suction chamber 26 are communicated with each other through a suction passage 32.
The suction port 31 is connected to an external refrigerant circuit (not shown).
A suction throttle valve 40 for adjusting the opening degree of the suction passage 32 is disposed in the middle of the suction passage 32.
Here, for convenience of explanation, the upstream side of the suction throttle valve 40 in the suction passage 32 is referred to as an upstream suction passage 32a, and the downstream side is referred to as a downstream suction passage 32b.

As shown in FIG. 2, the suction throttle valve 40 has a valve housing 41 that is a bottomless cylindrical member formed of a resin material.
The valve housing 41 has a housing upper part 42 that constitutes an upper part of the valve housing 41 and a housing lower part 43 that constitutes a lower part.
A suction valve body 50 is accommodated in the housing upper part 42, and a control valve element 55 is accommodated in the housing lower part 43.
In this embodiment, for convenience of explanation, in FIGS. 1 to 4, the housing upper part 42 side is the upper side of the suction throttle valve 40, and the housing lower part 43 side is the lower side.

The inner diameter of the housing top 42 that is larger than the inner diameter of the housing bottom 43.
An opening 44 communicating with the downstream suction passage 32b is formed on a side surface of the housing upper portion 42.
The outer periphery of the valve housing 41 is formed so as to substantially coincide with the wall surface of the suction passage 32, and the opening 44 of the housing upper portion 42 faces the suction passage 32 facing the suction chamber 26.
A suction side valve element 50 is accommodated inside the housing upper part 42, and the suction side valve element 50 has an outer diameter corresponding to the inner diameter of the housing upper part 42, and can reciprocate up and down in the housing upper part 42.
The suction side valve body 50 is a valve body that is guided to the lowest position at the maximum flow rate and guided to the uppermost position at the minimum flow rate.
The suction side valve body 50 includes a valve main body 51 and an annular side wall 52 that shields the entire opening 44 when positioned at the uppermost position in the housing upper part 42.

A cylindrical cap 53 corresponding to the inner diameter of the housing upper part 42 is inserted into the opening end of the housing upper part 42 facing upward.
The opening end of the cylindrical cap 53 facing upward is formed in a flange shape and is locked to the opening end of the housing upper part 42.
The lower end portion of the cylindrical cap 53 inserted into the housing upper portion 42 defines the uppermost position of the suction side valve body 50.
An annular protrusion 45 extending from the inner diameter side of the valve housing 41 toward the center side in the valve housing 41 is formed between the housing upper part 42 and the housing lower part 43, and the annular protrusion 45 is formed on the suction side. The lowest position of the valve body 50 is defined.

A control valve element 55 is accommodated in the housing lower part 43 so as to be reciprocally movable. The control valve element 55 has an outer diameter corresponding to the inner diameter of the housing lower part 43.
The uppermost position of the control valve body 55 is defined by the annular protrusion 45.
A coil spring 54 is interposed in the damper chamber 58 between the control valve body 55 and the suction side valve body 50, and the coil spring 54 always has a biasing force in a direction in which both of them are separated.

The control valve element 55 is a valve element guided to the uppermost position when the crank chamber 14 and the discharge chamber 27 are communicated with each other through the communication passage 28 (when the capacity control valve 29 is opened).
The control valve body 55 moves the suction side valve body 50 to the uppermost position when moved to the uppermost position.

When the control valve body 55 is moved to the uppermost position, the coil spring 54 increases the upward biasing force on the suction side valve body 50.
The damper chamber 58 communicates with the suction chamber 26 via a communication passage 59 shown in FIGS.

By the way, the opening end of the housing lower portion 43 is formed with a diameter-enlarged end portion 46 as a fitted portion that is larger than the diameter of the control valve body 55.
The enlarged diameter end portion 46 is a portion that holds the valve seat 60.
The valve seat 60 has a through hole 62 in the center, and the through hole 62 communicates with the branch path 33 branched from the communication path 28 in the rear housing 13.
The upper surface of the valve seat 60 defines the lowest position of the control valve body 55.

The housing lower portion 43 is provided with a rib 49 at a position slightly away from the enlarged diameter end portion 46, and an O-ring 65 is mounted between the rib 49 and the enlarged diameter end portion 46.
The O-ring 65 is provided to prevent the refrigerant gas having the crank pressure Pc from leaking to the suction side outside the suction throttle valve 40.
The control valve body 55 receives the crank pressure Pc of the crank chamber 14 from the branch passage 33 branched from the communication passage 28 in the rear housing 13 and reciprocates in the housing lower portion 43.

Incidentally, a lubricating oil passage 37 is formed between the upstream suction passage 32 a of the suction throttle valve 40 and the oil storage chamber 35 of the cylinder block 11.
The lubricating oil passage 37 has a cylinder block side through hole 11 a that communicates with the bottom side of the oil storage chamber 35 in the cylinder block 11, and a rear housing side through hole that communicates with the suction passage 32 upstream of the suction throttle valve 40 in the rear housing 13. 13b and a throttle through hole 38 in the valve forming mechanism 25.
The lubricating oil passage 37 is a passage for supplying the lubricating oil in the oil storage chamber 35 to the suction passage 32 on the upstream side of the suction throttle valve 40.
A filter member 36 is provided at the inlet of the cylinder block side through hole 11a on the oil storage chamber 35 side.
The filter member 36 is a member for separating foreign matters such as dust contained in the lubricating oil before the lubricating oil stored in the oil storage chamber 35 is passed through the lubricating oil passage 37.
The valve forming mechanism 25 of this embodiment includes a valve plate 25a, a suction valve forming plate 25b, a discharge valve forming plate 25c, and a retainer forming plate 25d.

In this embodiment, the diameter of the throttle through hole 38 provided in the valve forming mechanism 25 is set to be smaller than the diameter of the cylinder block side through hole 11a and the rear housing side through hole 13b. The lubricating oil supplied to the suction passage 32a receives a throttle.
For this reason, the throttle through hole 38 functions as a throttle in the lubricating oil passage 37, but does not prevent the lubricating oil passage 37 from being provided with the same diameter of the lubricating oil passage without providing the throttle through hole 38.
The throttle hole 38 also has a function of restricting the passage of refrigerant gas at the discharge pressure from the oil storage chamber 35 through the lubricating oil passage 37 to the suction passage 32 when no lubricating oil is stored in the oil storage chamber 35.

Next, the operation of the compressor according to the embodiment of the present invention will be described.
Based on the reciprocating motion of the piston 23 accompanying the rotational motion of the rotating shaft 15, the refrigerant gas in the suction chamber 26 is guided from the suction port of the valve forming mechanism 25 into the cylinder bore 22 by opening the suction valve, and the refrigerant gas in the cylinder bore 22 is introduced. Is compressed and discharged to the discharge chamber 27 by opening the discharge valve.
Most of the high-pressure refrigerant gas discharged to the discharge chamber 27 is guided to an external refrigerant circuit (not shown).

By changing the opening degree of the capacity control valve 29, the amount of refrigerant gas introduced from the discharge chamber 27 to the crank chamber 14 through the communication passage 28 and the refrigerant from the crank chamber 14 to the suction chamber 26 through the extraction passage 30 are changed. The balance with the derived amount of gas is controlled.
By controlling the balance between the amount of refrigerant gas introduced into the crank chamber 14 and the amount of refrigerant gas derived from the crank chamber 14, the crank pressure Pc of the crank chamber 14 is determined.
When the opening of the capacity control valve 29 is changed and the crank pressure Pc of the crank chamber 14 is changed, the differential pressure in the crank chamber 14 and the cylinder bore 22 through the piston 23 is changed, and the inclination angle of the swash plate 17 is changed. To do.
The stroke of the piston 23 is changed by changing the inclination angle of the swash plate 17, and the discharge capacity of the compressor is changed according to the change of the stroke of the piston 23.

For example, when the crank pressure Pc is lowered, the inclination angle of the swash plate 17 with respect to a plane perpendicular to the axial direction of the rotating shaft 15 increases, and the stroke of the piston 23 increases.
As the stroke of the piston 23 increases, the discharge capacity of the compressor increases.
Conversely, when the crank pressure Pc is increased, the inclination angle of the swash plate 17 decreases, the stroke of the piston 23 decreases, and the discharge capacity decreases.

During the operation of the compressor, the refrigerant gas discharged from the discharge chamber 27 contains mist-like lubricating oil.
The oil separator included in the compressor separates the lubricating oil from the refrigerant gas at the discharge pressure.
The separated lubricating oil is guided from the oil separator to the oil storage chamber 35, and is stored in the oil storage chamber 35 as shown in FIGS. 3 and 4 (the lubricating oil is indicated by “L” in FIGS. 3 and 4). .
The lubricating oil L stored in the oil storage chamber 35 is guided to the upstream suction passage 32 a through the lubricating oil passage 37.

Incidentally, the discharge capacity of the compressor is determined by the inclination angle of the swash plate 17 corresponding to the opening degree of the capacity control valve 29, but the suction throttle valve 40 is operated following the opening / closing operation of the capacity control valve 29. The
For example, in the process from the closed state to the open state of the capacity control valve 29, the inclination angle of the swash plate 17 gradually decreases and the minimum capacity operation (OFF operation) is performed.
The suction throttle valve 40 operates following this process, the control valve body 55 moves toward the uppermost position, and the control valve body 55 is attached via the coil spring 54 in the direction of closing the suction side valve body 50. Rush.

Further, since the differential pressure between the suction passage 32 facing the suction side valve body 50 and the damper chamber 58 is reduced, the suction side valve body 50 is moved so as to close the suction passage 32, and finally the suction passage 32 is sucked. It is closed by the side valve body 50.
The side wall 52 of the suction side valve body 50 opens and closes the opening 44 in accordance with the flow rate of the suction refrigerant, so that substantially the same state as that in which a variable throttle is provided between the suction passage 32 and the suction chamber 26 is obtained. Self-excited vibration of the intake valve due to pressure fluctuation is prevented.

As shown in FIG. 3, in the state where the suction side valve body 50 closes the opening 44, the lubricating oil L guided to the upstream side suction passage 32 a through the lubricant passage 37 is sucked upstream of the suction side valve body 50. It is stored in the passage 32a.
For this reason, most of the lubricating oil L introduced from the oil storage chamber 35 remains on the upstream side of the suction side valve body 50, and the lubricating oil L is not guided to the suction chamber 26, so that the lubricating oil L is contained in the crank chamber 14. Is not stored excessively.

Next, in the process of closing the capacity control valve 29 from the opened state, the inclination angle of the swash plate 17 gradually increases and the maximum capacity operation is performed.
In this process, the control valve body 55 moves from the uppermost position to the lowermost position, and the urging force of the coil spring 54 against the suction side valve body 50 does not act.
Even when the suction side valve body 50 closes the suction passage 32 during the maximum capacity operation, the refrigerant gas is sucked from the suction chamber 26 into the cylinder bore 22 at the maximum capacity, so that the suction facing the suction side valve body 50 is performed. The differential pressure between the passage 32 and the damper chamber 58 is increased.
For this reason, the suction side valve body 50 moves downward so as to open the suction passage 32.

In a state where the suction side valve body 50 opens the opening 44, the lubricating oil L guided to the upstream side suction passage 32a through the lubricant passage 37 is from the upstream side of the suction side valve body 50 as shown in FIG. It passes through the opening 44.
Therefore, most of the lubricating oil L introduced from the oil storage chamber 35 is guided to the crank chamber 14 through the suction chamber 26.

The compressor according to the first embodiment has the following effects.
(1) When the suction throttle valve 40 opens the suction passage 32, the lubricating oil L in the oil storage chamber 35 is introduced into the suction chamber 26 through the lubricating oil passage 37, the suction passage 32, and the suction throttle valve 40. When closing the suction passage 32, the lubricating oil L guided to the upstream suction passage 32a through the lubricant passage 37 is stored in the upstream suction passage 32a. For this reason, when the intake throttle valve 40 closes the intake passage, the separated lubricating oil L is not excessively supplied to the crank chamber 14.

(2) Since the lubricating oil is stored in the upstream suction passage 32a of the intake throttle valve 40 after the compressor is stopped, the lubricating oil may be excessively stored in the crank chamber 14 in the compressor after the stop. However, when the compressor is started again, the stirring of the lubricating oil and the oil compression by the rotating elements such as the swash plate 17 are suppressed. For this reason, the durability fall and performance fall of a compressor accompanying the temperature rise of lubricating oil stirring can be suppressed.
(3) By returning the separated lubricating oil to the suction passage 32 through the lubricating oil passage 37, a temperature drop of the lubricating oil can be promoted, thereby improving the durability of the compressor.
(4) Since lubricating oil enters the clearance between the suction side valve body 50 and the inner peripheral surface of the valve housing 41 by supplying lubricating oil to the upstream suction passage 32a of the suction throttle valve 40, the oil in the suction throttle valve 40 A seal can be realized. The suction throttle valve 40 is operated by the differential pressure between the crank chamber pressure and the suction pressure. However, leakage between the crank chamber 14 and the suction chamber 26 can be reduced by the oil seal, thereby improving controllability and performance. Can do.
(5) When the compressor is of a variable capacity type, if excessive lubricating oil is stored in the crank chamber 14, not only the temperature rises due to shear heat but also the swash plate causes the lubricating oil to return to the maximum capacity side. 17 and the return of the swash plate 17 is delayed. By prevented from being excessively stored lubricating oil in the crank chamber 14, the return delay of the swash plate 17 can no camphor.

(Second Embodiment)
Next, the compressor which concerns on 2nd Embodiment is demonstrated based on FIGS.
The compressor of this embodiment is different from that of the first embodiment in that an opening / closing valve is provided in the lubricating oil passage.
In this embodiment, the description of the first embodiment is used for elements that are common or similar to those in the first embodiment, and common or similar elements are denoted by common reference numerals.

As shown in FIG. 5, a lubricating oil passage 71 is formed between the upstream suction passage 32 a of the suction throttle valve 40 and the oil storage chamber 72 of the cylinder block 11.
The lubricating oil passage 71 has a cylinder block side through hole 11 a that communicates with the bottom side of the oil storage chamber 72 in the cylinder block 11, and a rear housing side through hole that communicates with the suction passage 32 upstream of the suction throttle valve 40 in the rear housing 13. 13b and through holes A, C, D, and E in the valve forming mechanism 73.
In this embodiment, the cylinder block side through hole 11a communicates with the oil storage chamber 72 without passing through the filter member.
The valve forming mechanism 73 of this embodiment includes a valve plate 73a, a suction valve forming plate 73b, a discharge valve forming plate 73c, a retainer forming plate 73d, and a gasket 73e.
The gasket 73e is interposed between the cylinder block 11 and the suction valve forming plate 73b.

In the valve forming mechanism 73 of this embodiment, as shown in FIG. 6, the diameters of the cylinder block side through hole 11a and the rear housing side through hole 13b are formed in the valve plate 73a, the discharge valve forming plate 73c, the retainer forming plate 73d, and the gasket 73e. Through holes A, C, D, and E having the same diameter are formed.
As shown in FIGS. 6 and 7, a reed valve 74 as an on-off valve is formed on the intake valve forming plate 73b.
The reed valve 74 is a valve that substantially closes the through hole E of the gasket 73e in a state where the reed valve 74 is not bent (a state indicated by a solid line in FIG. 6).
The reed valve 74 is generally closed with the through hole E of the gasket 73e in a state where the reed valve 74 is not bent. Has been.

On the other hand, the valve plate 73a has a notch K corresponding to the bending of the reed valve 74.
The reed valve 74 is also a valve that substantially closes the through hole A of the valve plate 73a when the maximum opening with respect to the through hole E is reached (indicated by a two-dot chain line in FIG. 6).
When the reed valve 74 substantially closes the through hole A of the valve plate 73a, the through hole A is set to a condition that allows the lubricating oil to pass through slightly.
The reed valve 74 is a valve that bends according to the pressure difference between the pressure in the oil storage chamber 72 and the internal pressure in the upstream suction passage 32a.
In this embodiment, since the reed valve 74 that is not bent substantially closes the through hole E of the gasket 73 e, the through hole E of the gasket 73 e corresponds to the first valve hole in the lubricating oil passage 71.
Further, the through hole A of the valve plate 73 a corresponds to the second valve hole in the lubricating oil passage 71.

In this embodiment, when the differential pressure between the pressure in the oil storage chamber 72 and the internal pressure in the upstream suction passage 32a is small, the reed valve 74 does not bend, so the through hole E that is the first valve hole is substantially closed.
At this time, the flow rate of the lubricating oil passing through the lubricating oil passage 71 is suppressed.
When the differential pressure between the pressure in the oil storage chamber 72 and the internal pressure in the upstream suction passage 32a increases, the reed valve 74 opens the through hole E, so that the flow rate of the lubricating oil increases.
However, when the differential pressure is further increased, the reed valve 74 is bent to the maximum, and the reed valve 74 in a state of being bent to the maximum closes the through hole A that is the second valve hole.
For this reason, the flow rate of the lubricating oil passing through the lubricating oil passage 71 is suppressed.
FIG. 8 is a graph showing the relationship between the opening of the reed valve 74 with respect to the through hole E and the passage area of the lubricating oil passage 71.

Further, since the reed valve 74 is provided in the lubricating oil passage 71, when the lubricating oil is not stored in the oil storage chamber 72, the refrigerant gas passes through the lubricating oil passage 71 from the oil storage chamber 72 to the suction passage 32 and passes through the refrigerant gas. (Gas path phenomenon) is more reliably regulated than when a throttle passage is used.
Although the refrigerant flow rate is low and the lubricating oil separation capability is low as in the high load low speed operation of the compressor, the discharge pressure becomes high due to the high load, and the pressure in the oil storage chamber 72 and the upstream suction passage 32a are increased. Even in a state where the pressure difference from the pressure of the oil is large and the flow rate of the lubricating oil passing through the lubricating oil passage 71 is large, the reed valve 74 can be closed substantially and the flow rate of the lubricating oil can be suppressed. , Gas path can be prevented.
Furthermore, since the reed valve 74 can control and throttle the flow rate of the lubricating oil, it is not necessary to provide a throttle passage having a small diameter in the lubricating oil passage 71, and thus there is almost no possibility of clogging with foreign matter. The conventionally required filter member is not necessary.

(Third embodiment)
Next, a compressor according to a third embodiment will be described with reference to FIG.
The compressor according to the third embodiment is a fixed capacity compressor having a constant discharge capacity.
The compressor shown in FIG. 9 includes a cylinder block 81 having a plurality of cylinder bores 82.
A front housing 83 is joined to the front end of the cylinder block 81, and a rear housing 84 is joined to the rear end of the cylinder block 81.
Between the rear housing 84 and the cylinder block 81, a valve plate 98a, a suction valve forming plate 98b, a discharge valve forming plate 98c, and a retainer forming plate 98d constituting the valve forming mechanism 98 are interposed.

A rotation shaft 87 is rotatably supported at the center of the cylinder block 81.
A single-headed piston 85 is accommodated in the cylinder bore 82 of the cylinder block 81 so as to be able to reciprocate.
A crank chamber 86 is formed in the cylinder block 81, and a swash plate 93 that rotates integrally with the rotary shaft 87 is accommodated in the crank chamber 86.
The piston 85 is anchored to the outer peripheral portion of the swash plate 93 via the shoe 88, and the swash plate 93 slides with respect to the shoe 88.

A suction chamber 89 is defined on the inner periphery of the rear housing 84, and a discharge chamber 90 is formed on the outer periphery of the suction chamber 89.
In this embodiment, a suction passage 91 communicating with the suction chamber 89 is formed in the rear housing 84, and a suction throttle valve 92 is provided in the middle of the suction passage 91.
The suction throttle valve 92 has a valve body 94 that is opened and closed in accordance with a differential pressure between the upstream suction passage 91 a that is upstream of the suction throttle valve 92 and the suction chamber 89.
A downstream suction passage 91 b, which is upstream of the suction throttle valve 92, communicates with the suction chamber 89.
An oil storage chamber 95 is provided on the outer periphery of the cylinder block 81, and the oil storage chamber 95 stores lubricating oil contained in refrigerant gas having a discharge pressure separated by an oil separator (not shown).

A lubricating oil passage 97 that communicates between the oil storage chamber 95 and the upstream suction passage 91a is formed.
The lubricating oil passage 97 has a cylinder block side through hole 81 a communicating with the bottom side of the oil storage chamber 35 in the cylinder block 81, and a rear housing side through hole communicating with the suction passage 91 upstream of the suction throttle valve 92 in the rear housing 84. 84a and a throttle hole 99 in the valve forming mechanism 98.
The lubricating oil passage 97 is a passage for supplying the lubricating oil in the oil storage chamber 95 to the suction passage 91 (upstream suction passage 91a) on the upstream side of the suction throttle valve 92.
The valve forming mechanism 98 of this embodiment includes a valve plate 98a, a suction valve forming plate 98b, a discharge valve forming plate 98c, and a retainer forming plate 98d.
The diameter of the throttle hole 99 provided in the valve forming mechanism 98 is set to be smaller than the diameters of the cylinder block side hole 81a and the rear housing side hole 84a.

In this embodiment, even if the compressor is a fixed capacity compressor, when the suction passage 91 is blocked by closing the valve body 94 of the suction throttle valve 92, the refrigerant gas to the suction chamber 89 through the suction passage 91 is blocked. Is interrupted.
The lubricating oil supplied to the upstream suction passage 91a through the lubricating oil passage 97 is stored in the upstream suction passage 91a. In this case, the separated lubricating oil is not excessively supplied to the suction chamber 89 and the crank chamber 86 which are low pressure regions.

  The present invention is not limited to the first to third embodiments described above, and various modifications can be made within the scope of the gist of the invention.

  In the first to third embodiments, the suction throttle valve is a valve in which the suction side valve body and the control valve body are connected via a coil spring. For example, instead of the coil spring, a connection member is used. The suction side valve body and the control valve body may be connected, and the suction throttle valve may be any suction throttle valve in which the valve body moves due to the differential pressure between the crank chamber and the suction pressure.

  In the above first to third embodiments, the suction throttle valve is a suction throttle valve that adjusts the opening of the suction passage based on the differential pressure between the suction pressure and the crank chamber pressure. And a suction throttle valve that opens and closes the suction passage based on the differential pressure between the suction chamber and the suction chamber.

In the second embodiment described above, when the reed valve 74 closes the through hole E of the gasket 73e which is the first valve hole, the lubricating oil slightly passes through the through hole E. When the hole E is closed, the flow of the lubricating oil in the through hole E may be completely blocked.
In the second embodiment, the reed valve 74 is formed on the suction valve forming plate 73b. However, a reed valve may be provided on the discharge valve forming plate 73c.
Further, the notch K formed in the valve plate 73a is a notch having a U-shaped cross section, but the cross-sectional shape of the notch can be freely changed according to the opening degree setting of the reed valve 74.

It is a longitudinal section showing a clutchless type variable capacity compressor concerning a 1st embodiment. It is a longitudinal cross-sectional view which shows the principal part of the variable capacity compressor which concerns on 1st Embodiment. It is a longitudinal cross-sectional view of the principal part which shows the operation | movement of a suction throttle valve when a capacity | capacitance control valve opens, and the flow of lubricating oil. It is a longitudinal cross-sectional view of the principal part which shows the operation | movement of a suction throttle valve when a capacity | capacitance control valve is closed, and the flow of lubricating oil. It is a longitudinal cross-sectional view which shows the principal part of the variable capacity compressor which concerns on 2nd Embodiment. It is a longitudinal cross-sectional view which expands and shows the principal part of the lubricating oil channel | path which concerns on 2nd Embodiment. It is a front view of the suction valve formation board which provided the reed valve concerning a 2nd embodiment. 4 is a graph showing the relationship between the opening degree of the reed valve with respect to the through hole E and the passage area of the lubricating oil passage. It is a side view which cuts and shows the fixed capacity compressor which concerns on 3rd Embodiment longitudinally.

Explanation of symbols

11, 81 Cylinder block 11a, 81a Cylinder block side through hole 13, 84 Rear housing 13a, 84a Rear housing side through hole 15, 87 Rotating shaft 17, 93 Swash plate 23, 85 Piston 25, 73, 98 Valve forming mechanism 26, 89 Suction chamber 29 Capacity control valve 31 Suction ports 32, 91 Suction passages 32a, 92a Upstream suction passage 33 Branch passage 34 Flange members 35, 72, 95 Oil storage chamber 36 Filter members 37, 71, 97 Lubricating oil passages 38, 99 Restriction Through hole 40, 92 Suction throttle valve 41 Valve housing 44 Opening 50 Suction side valve element 73e Gasket 74 Reed valve A, C, D, E Through hole K Notch L Lubricating oil

Claims (6)

A suction chamber into which a refrigerant gas is sucked through a suction port connected to an external refrigerant circuit, a discharge chamber from which the refrigerant gas is discharged by being connected to the external refrigerant circuit, and a discharge chamber are discharged from the discharge chamber. the lubricating oil separated from refrigerant gas under a discharge pressure to a compressor having a lubricant storage chamber for storing,
The compressor further includes
A suction passage communicating the suction port and the suction chamber;
A suction throttle valve for adjusting an opening degree of the suction passage based on a differential pressure acting on the valve body,
Compressor characterized by comprising a lubricating oil passage through which lubricating oil in the oil storage chamber upstream of the suction throttle valve in the suction passage.   The compressor according to claim 1, wherein the lubricating oil passage has an on-off valve that controls a flow rate of the lubricating oil in the lubricating oil passage. 3. The reed valve that opens and closes the lubricating oil passage according to a pressure difference between a pressure in the oil storage chamber and a pressure upstream of the suction throttle valve in the suction passage. Compressor. The lubricating oil passage has a first valve hole and a second valve hole that are opened and closed by the open / close valve, and the open / close valve in a closed state with respect to the first valve hole passes through the first valve hole. The compression according to claim 3, wherein the flow rate of the lubricating oil is suppressed, and the on-off valve in a maximum open state with respect to the first valve hole suppresses the flow rate of the lubricating oil passing through the second valve hole. Machine.   Between the housing member having a suction chamber and the cylinder block, a gasket, a valve forming body forming a suction valve, and a valve plate are interposed, the first valve hole is formed in the gasket, and the second valve hole is formed. The compressor according to claim 3 or 4, wherein the valve plate is formed on the valve plate, the reed valve is formed on the valve forming body, and a maximum opening degree is defined by the valve plate. A suction chamber into which a refrigerant gas is sucked through a suction port connected to an external refrigerant circuit, a discharge chamber from which the refrigerant gas is discharged by being connected to the external refrigerant circuit, and a discharge chamber are discharged from the discharge chamber. An operating method of a compressor having an oil storage chamber for storing lubricating oil separated from refrigerant gas at a discharge pressure,
Opening and closing a suction throttle valve provided in a suction passage communicating the suction port and the suction chamber based on a differential pressure acting on the valve body;
Passing the separated lubricating oil upstream of the suction throttle valve in the suction passage;
Supplying the lubricating oil to the suction chamber through the suction throttle valve by opening the suction throttle valve;
A method of operating a compressor, wherein the supply of the lubricating oil to the suction chamber is suppressed by closing the suction throttle valve.

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